Binding toe-piece for gliding board

ABSTRACT

Toe-piece for a boot on a gliding board including a chassis affixed to the gliding board; a body movable on the chassis; a sole-clamp movable on the body; a lateral release mechanism including a first elastic mechanism to return the sole clamp to engagement with the boot; a vertical retention mechanism having a second elastic mechanism arranged to continuously exert a return force on the body to bring the sole-clamp toward the lower surface of the chassis, the return force pressing the sole-clamp on the boot; at least one cam kinematically inserted between the second elastic mechanism and either the chassis or the body, the cam being shaped to modify, in relation to the chassis, the direction of the return force exerted by the second elastic mechanism on the body to attenuate a variation in the pressing force when the sole-clamp is away from the lower surface of the chassis.

CROSS-REFERENCE TO RELATED APPLICATION

This application is based upon French Patent Application No. FR 2001947, filed Feb. 27, 2020, the disclosure of which is herebyincorporated by reference thereto in its entirety, and the priority ofwhich is claimed under 35 U.S.C. § 119.

BACKGROUND 1. Field of the Invention

The present invention relates to the field of boot bindings on a glidingboard. The invention relates more particularly to a binding toe-piece,as well as a binding or a gliding board equipped with such a toe-piece.The invention has a particularly advantageous application in the fieldof skiing.

2. Background Information

A boot binding on a gliding board, such as a ski or a snowboard,generally comprises a front retaining device, referred to as atoe-piece, and a rear retaining device, referred to as a heel-piece. Theboot is inserted between the tope piece and the heel-piece, theseelements being attached to the gliding board. The toe-piece and theheel-piece are each equipped with stopping means acting on the boot soas to block the displacement of the boot in relation to the glidingboard along the three longitudinal, vertical, and transverse directions.Thus, the combined action of these two retaining devices makes itpossible to affix the boot to the gliding board, when the boot isengaged with the binding.

Various solutions exist for making a toe-piece or a heel-piece. Forexample, patent documents EP-A-0 241 360, EP-A-1 151 765, and EP-A-2 174695 describe various embodiments of toe-pieces and heel-pieces. In theseillustrations, the toe-piece incorporates a sole-clamp comprising twoV-shaped wings, the branches of which partially cover a front extensionof the boot, along a vertical direction. Furthermore, the sole of theboot, i.e., the lower surface of the boot, presses on a support platefixed to the gliding board. Consequently, the vertical immobilization ofthe boot in the area of the toe-piece is achieved by a double contactbetween the upper surface of the front extension of the boot and thewings of the toe-piece, on the one hand, and the sole of the boot andthe support plate, on the other hand.

For safety reasons, the toe-piece and the heel-piece typicallyincorporate a safety mechanism making it possible to release thebinding, if necessary. This mechanism enables the foot of the user to befreed to avoid injury during accidental transverse and/or verticalmovement of the foot. This may occur in the event of a fall or othercircumstances to prevent injury to the foot when the forces exerted onthe boot exceed predetermined values. Safety mechanisms for thetoe-piece are also described in the above-cited documents.

Various types of ski boots exist, including boots for alpine skiing andboots for ski touring. These two categories of boots are characterizedby the NF ISO 5355 and NF ISO 9523 standards, respectively, anddistinguish over one another by the dimensions of the portionsinterfacing with the elements of the binding. The dimensions of theinterfacing portions vary from one category to the other and, therefore,the bindings are generally designed or configurable to receive a singleboot category.

Certain toe-pieces comprise a mechanism allowing for elastic adjustmentof the height, or vertical positioning, of their wings. This elasticmechanism is used to compensate for small dimensional variations due tothe manufacturing tolerances in a boot of the same category. However,these toe-pieces do not allow sufficient height adjustment to make thebinding compatible with alpine ski boots and ski touring bootsautomatically (without adjustment by the user).

Similarly, there are bindings in which the support plate interfacingwith the sole of the boot is mounted on an elastic mechanism in order tocompensate for the dimensional variations inherent in a particular bootcategory. These toe-pieces also do not allow making the bindingcompatible with alpine ski boots and ski touring boots automatically(without adjustment by the user).

Other toe-pieces are divided into two portions, the portionincorporating the wings being adjustable in height, via an adjustmentscrew, in relation to the other portion fixed to the ski. A toe-piece ofthis type enables the binding to be configured alternately for alpineski boots and for ski touring boots. However, a toe-piece of this typeis complex, expensive, and hardly compatible with a mechanism making itpossible to compensate for the dimensional variations inherent in a bootcategory. This design does not make it possible to cover largedimensional variations. Furthermore, the height adjustment of the wingsfor compatibility with a hoot category is not straightforward, becausethe adjustment is carried out continuously and without referencemarkings, by screwing the screw. It is therefore not easy to adjust theheight of the wings correctly for a particular boot category. Moreover,this type of adjustment to adapt to a boot category is not convenientfor the user as it requires moving the portion incorporating the wingsover a long length of travel, which involves turning the screwdriverseveral times.

Alternatively, other toe-pieces, also comprised of two portions, make itpossible to modify the vertical position of the support plate inrelation to the portion incorporating the wings. The disadvantages aresimilar to those of the previous constructions, in which it is theportion incorporating the wings that is movable.

For these two-portion toe-pieces, the adjustment is generally done withthe boots and often requires a plurality of operations to adjust thetightening.

SUMMARY

Therefore, the present invention provides a user-friendly and reliablesolution for automatically making the binding compatible with bootshaving various dimensions with respect to their interface with thebinding, without adjustment by the user.

The present invention also provides a user-friendly and reliablesolution for enabling alpine ski boots and ski touring boots to be usedon the same binding.

The invention further provides a binding that is automaticallycompatible with a plurality of boot categories without significantlydisrupting the operation of the lateral release mechanism.

The other objects, characteristics and advantages of the presentinvention will become apparent from the following description and theannexed drawings. It is to be understood that other advantages can beincorporated.

To achieve these objects, according to one embodiment, a retainingdevice, for example a toe-piece, is provided for binding a boot on agliding board, comprising:

-   -   a chassis having an interface, typically a lower surface,        configured to be affixed to the gliding board;    -   a body movably mounted on the chassis;    -   a sole-clamp movably mounted on the body and capable of coming        into contact with an upper surface and at least one lateral        portion of a front or rear portion of the boot, when the boot is        engaged with the binding;    -   a lateral release mechanism comprising at least one first        elastic mechanism acting on the sole-clamp to return it back to        a configuration of engagement with the boot;    -   a vertical retention mechanism comprising a second elastic        mechanism, distinct from the first elastic mechanism, arranged        so as to continuously, or always, exert a return force on the        body in order to bring the sole-clamp back toward the lower        surface of the chassis, this return force producing a force        pressing the sole-clamp on the boot, when the boot is engaged        with the binding.

The toe-piece comprises at least one cam, kinematically interposedbetween the second elastic mechanism and either the chassis or the body.The cam is shaped to modify the direction of the return force exerted bythe second elastic mechanism on the body, as a function of the positionof the body in relation to the chassis, so as to attenuate a variationin the pressing force when the sole-clamp is away from the interface ofthe chassis.

Due to this construction, the pressing force exerted by the sole-clampon the boot remains controlled regardless of the dimensions of theportion of the boot interfacing with the binding. For example, if aninterface having a greater thickness, taken along a vertical direction,is used, as is the case for ski touring boots, the cam makes it possibleto control the pressing force and to reduce the frictional forcesbetween the sole-clamp and the boot during lateral release, therebyimproving the reliability of the lateral release. Thus, the inventionmakes it possible to significantly improves the safety of the user of aself-configuring binding.

Boots having variable dimensions for interfacing with the binding canthen be used with a binding equipped with this toe-piece. Typically, thepresent invention enables both alpine ski boots and ski touring boots tobe used with the same binding, these two categories distinguishing overone another in particular by the dimensions of the portions interfacingwith the toe-piece; these portions are referred to as the sole below forthe sake of brevity. Irrespective of the type of boot used, the lateralrelease force remains controlled.

For a toe-piece of this type, in which the displacement of thesole-clamp is energized, the distancing of the sole-clamp in relation tothe gliding board causes an increase in the compression of the secondelastic mechanism, and thus causes an increase in the return forcegenerated by this second elastic mechanism. In the absence of the cam,this increase in the return force would result in a very significantincrease in the pressing force exerted by the sole-clamp on the boot.This pressing force would generate friction between the sole-clamp andthe boot. This friction would oppose the movability of the sole-clamp inrelation to the body, and thus would oppose the lateral release and,ultimately, the release of the boot. Therefore, the release of the bootwould not be controlled, and the safety of the user would besubstantially degraded, in a configuration in which the sole-clamp wouldbe away from the gliding board.

The claimed construction adds a cam that tends to reduce the increase inthe pressing force when the sole-clamp is moved away from the glidingboard. In other words, this makes it possible, for example, to have asmall variation in the pressing force, or at least a controlledvariation, irrespective of the position of the sole-clamp.

Depending on the configuration of the toe-piece, and in particular theshape of the cam and the dimensioning of the second elastic mechanism,the pressing force can be provided to remain constant regardless of theposition of the sole-clamp in relation to the gliding board. Thus,regardless of the type of boots used, it is possible to obtain a lateralrelease force that remains substantially constant.

Optionally, the toe-piece can further have at least any of the followingcharacteristics, which can be taken separately or in combination.

According to one example, the body is pivotally mounted on the chassisabout an axis of rotation that is crosswise to a longitudinal axis ofthe chassis, the cam being dimensioned so as to modify the direction ofthe return force exerted by the second elastic mechanism on the body, sothat the distance between the direction of the return force and the axisof rotation of the body differs as a function of the angle ofinclination of the body in relation to the chassis. The inclination ofthe body in relation to the chassis is measured in a vertical planepassing through the longitudinal axis of the chassis.

According to one example, the axis of rotation of the body is positionedin the area of the upper portion of the body, above the first elasticmechanism of the lateral release mechanism.

According to one example, the cam and the vertical retention mechanismare shaped such that the pressing force Fp does not vary by more than20%, preferably does not vary by more than 10%, irrespective of theposition of the sole-clamp in relation to the body. This makes itpossible to avoid a substantial increase in the intensity of the lateralrelease force that must be exerted on the sole-clamp, i.e., thethreshold value enabling the toe-piece to switch to the releaseconfiguration in order to release the boot.

According to one example, the second elastic mechanism is arranged so asto act continuously, or always, on the body, irrespective of theposition of the sole-clamp in relation to the body.

According to one example, the sole-clamp exerts on the first elasticmechanism of the lateral release mechanism an action that is oppositethat exerted by the first elastic mechanism on the sole-clamp. Thesecond elastic mechanism is arranged so as to act on the bodyindependently of the action of the sole-clamp on the first elasticmechanism of the lateral release mechanism. The displacement of thesole-clamp in relation to the body does not act on the second elasticmechanism. Thus, the first elastic mechanism and second elasticmechanism operate independently.

According to one example, the first elastic mechanism is configured tobe alternately compressed and relaxed along a first working axis, thesecond elastic mechanism is configured to be alternately compressed andrelaxed along a second working axis, the second working axis beingmisaligned with respect to the first working axis. According to anexample of embodiment, the first and second working axes are containedin the same vertical plane. However, they are not parallel.

According to one example, the second elastic mechanism acts directly ona piston capable of translating into a housing of the body, a portion ofthe piston forming a first profile of the cam.

According to one example, the sole-clamp comprises two wings, each wingbeing pivotally mounted on the body. In one example, each wing pivotsindependently of the other wing on the body.

According to one example, the cam is dimensioned such that the returntorque exerted on the body, and characterized by the product of theintensity of the return force multiplied by the distance between thedirection of the return force and the axis of rotation of the body, is,when the sole-clamp is away from the gliding board, identical, atapproximately 20%, preferably at approximately 10% to this return torquewhen the sole-clamp is close to the lower surface of the chassis.

According to one example, the lateral release mechanism comprises anadjustment device configured to adjust a threshold value of a releaseforce to be applied by the boot to the lateral release mechanism inorder to cause the sole-clamp to switch from an engagement configurationto a release configuration. According to one example, the toe-piece alsocomprises a compensation mechanism configured to exert an additionalreturn force on the body, the intensity of the additional return forcebeing a function of such adjustment. The pressing force is then afunction of the return force exerted by the second elastic mechanism andof the additional return force exerted by the compensation mechanism.According to one example, the compensation mechanism is configured toincrease the pressing force when the adjustment increases the thresholdvalue of the release force. Thus, if the user wishes to be more firmlysupported laterally, he will adjust the adjustment device in thatdirection. As a result, the sole-clamp pressing force on the boot willalso increase automatically. This further improves the safety providedby the toe-piece. Thus, the proposed toe-piece makes it possible to:

-   -   maintain a constant pressing force, regardless of the boot used,        when the user wishes to preserve the adjustment of the threshold        value of the release force; and    -   vary this pressing force as a function of the release threshold        value adjusted by the user, typically by increasing the pressing        force, when the user increases the lateral release threshold        value.

According to one example, the second elastic mechanism is carried by thebody. According to one example, the cam has a first cam profile affixedto the body in rotation about the axis of rotation, and a second camprofile affixed to the chassis. According to one example, the first camprofile is translationally mounted on the body. According to analternative example, the second elastic mechanism is carried by thechassis. According to one example, the cam has a first cam profileaffixed to the body in rotation about the axis of rotation, and a secondcam profile carried by the chassis and preferably being slidably mountedon the chassis.

Another aspect relates to a boot binding on a gliding board, comprisinga retaining device as described above and a complementary retainingdevice, the retaining device being either a toe-piece or a heel-pieceand the complementary retaining device also being either a toe-piece ora heel-piece, respectively.

Another aspect relates to a gliding board equipped with at least onetoe-piece according to the preceding paragraphs.

BRIEF DESCRIPTION OF DRAWINGS

The objects, characteristics, and advantages of the invention will bebetter understood from the detailed description that follows, withreference to the annexed drawings illustrating, by way of non-limitingembodiments, how the invention can be carried out, and in which:

FIG. 1 is a perspective view of a toe-piece according to an exampleembodiment of the present invention and of a portion of a gliding boardequipped with such a toe-piece.

FIG. 2 is another perspective view of the toe-piece shown in FIG. 1 andof a portion of a boot.

FIG. 3 is an exploded perspective view of the toe-piece illustrated inFIG. 1.

FIG. 4 is another exploded perspective view of the toe-piece illustratedin FIG. 1.

FIG. 5 is a horizontal cross-sectional view of the toe-piece illustratedin FIG. 1.

FIG. 6 is a view of the toe-piece illustrated in FIG. 1, in verticalcross-section and passing through a median axis of the toe-piece. Thetoe-piece is shown in the lower position, that is to say in a positionin which it is not biased by a boot.

FIG. 7 corresponds to FIG. 6, a portion of a first boot category beingshown in engagement with the toe-piece.

FIG. 8 corresponds to FIG. 6, a portion of a second hoot category,different from the first boot category, being shown in engagement withthe toe-piece.

FIG. 9A is a graph illustrating the pressing force as a function of theinclination angle of the body in relation to the chassis for a pluralityof adjustment values of the lateral release threshold.

FIG. 9B is a graph illustrating the lateral release force as a functionof the inclination angle of the body in relation to the chassis for aplurality of adjustment values of the lateral release threshold.

FIG. 10 is a view of a toe-piece according to another embodiment, invertical cross-section and passing through a median axis of thetoe-piece. The toe-piece is shown in a lower position, that is to say ina position in which it is biased by a first boot category.

FIG. 11 is a view identical to that of FIG. 10, but in which thetoe-piece is in the upper position, that is to say in a position inwhich it is biased by a second hoot category.

The drawings are given as examples and are not limiting to theinvention. They constitute schematic representations intended tofacilitate the understanding of the invention and are not necessarily atscale for practical applications.

DETAILED DESCRIPTION

The following detailed description makes use of terms such as“horizontal”, “vertical”, “longitudinal”, “transverse”, “upper”,“lower”, “top”, “bottom”, “front”, “rear”, “interior”, “exterior”. Theseterms should be considered as relative terms in relation to the normalposition of the binding/boot/gliding board assembly, and to the normaldirection of forward displacement of the user of the assembly. Forexample, the terms “horizontal” and “longitudinal” correspond to themain direction of extension of the gliding board. The surface of thegliding board intended to receive the binding is oriented toward the“top” and the surface of the gliding board intended to rest on the snowis oriented toward the “bottom”. For illustrative and non-limitingpurposes, reference may be made below to a ski as the gliding board orto a skier as the user.

A reference point will also be used, of which the longitudinal orrear/front direction corresponds to the X axis, the transverse orright/left direction corresponds to the Y axis, and the vertical ordown/up direction corresponds to the Z axis.

Furthermore, the term “engagement” refers to the affixation of the bootto the binding, and the term “release” refers to the separation of theboot from the binding. More precisely, the “lateral release” correspondsto the release of the binding by a lateral force of the boot on thebinding. In the embodiments described below, the lateral release isachieved in the area of the toe-piece, by a lateral displacement of thefront of the boot. Typically, this lateral displacement is caused by theuser's fall. An engagement configuration corresponds to a configurationfor which the boot is engaged with the binding.

By “release level” of the binding is meant a measurement of the value ofthe force to be exerted by the boot on an element of the binding inorder to release the boot from the binding via the release mechanism.This value may be marked on the binding in accordance with the ISO 9462standard or one of its subsequent editions. It may correspond to anadjustment value or to a pre-adjustment value of the associated binding.For the release level to be efficient, the spacing of the bindingelements must be adapted to the boot intended to be engaged with thebinding, in order to ensure proper engagement of the binding.

The terms “DIN adjustment” or “DIN value”, with respect to the release,refer to the adjustment or the value that is set by a German Institutefor Standardization (DIN stands for “Deutsches Institut für Normung”). ADIN-certified binding thus meets certain standards. In particular, allDIN-certified bindings have equivalent adjustments. In particular, therelease level of a binding of one brand adjusted to a DIN value equal to6 will be the same as that of a binding of another brand adjusted to thesame DIN value if both bindings are DIN-certified.

In the following the description, the term “on” does not necessarilymean “directly on”. Thus, when a part or a member A is said to takesupport “on” a part or a member B, this does not mean that the parts ormembers A and B are necessarily in direct contact with one another.These parts or members A and B can either be in direct contact with ortake support on one another through one or more other parts. The same istrue for other expressions such as the expression “A acts on B”, forexample, which may mean that “A acts directly on B”, or that “A acts onB through one or more other parts.”

In the context of the instant description, the expression “kinematicallyinserted between” does not necessarily mean in “contact with”. Thus, ifa part A is kinematically inserted between a part B and a part C, thisdoes not mean that A and B are necessarily in direct contact, or that Aand C are necessarily in direct contact. This means that a movement or aforce of the part B or of the part C, respectively, can be at leastpartially transmitted to the part C or to the part B, respectively,through the part A.

In the instant description, the term “movable” corresponds to arotational movement or a translational movement or even a combination ofmovements, for example the combination of a rotation and a translation.

In the instant description, the term “to attenuate” is equivalent to theterm “to reduce”. It can mean to reduce partially or completely, i.e.,to cancel.

In the instant description, when two parts are said to be distinct, itmeans that these parts are separate. They are:

-   -   positioned at a distance from one another, and/or    -   movable in relation to one another, and/or    -   affixed to one another through attached elements; this        affixation may or may not be removable.        A unitary part cannot therefore be comprised of two distinct        parts.

In the instant description, the term “affixed” used to qualify theconnection between two parts means that the two parts areconnected/fixed in relation to one another, according to all degrees offreedom, at least for a configuration of use, unless it is explicitlyspecified otherwise. For example, if two parts are said to betranslationally affixed to one another along an X direction, this meansthat the parts can be movable, possibly according to several degrees offreedom, to the exclusion of the freedom in translation along the Xdirection. In other words, if one part is displaced along the Xdirection, the other part performs the same displacement.

In the instant description, an elastic mechanism can be considered to bean object that has the ability to deform under applied force and thenuse such force to return to its original shape. Conversely, an objectthat can return to its original shape after being deformed by appliedforce, can be considered an elastic mechanism. An elastic mechanism canbe a spring, for example, such as but not limited to, a coil spring, anelastic washer such as a Belleville washer, elastomer, rubber, etc.

In the instant description, the term “cam device” corresponds to adevice comprising at least:

-   -   a first so-called guide surface, also referred to as a cam        profile, carried by a first part, and    -   a second surface carried by a second part.        Either one of the first and second parts is movable, at least in        rotation in relation to a chassis about an axis of rotation. The        first and second surfaces are configured such that, when the        movable part is rotationally driven in relation to the chassis,        the projected distance (D1, D2) between the axis of rotation        (Y122) and the normal direction (Fr1, Fr2) at the point of        contact between these two surfaces varies.

A non-limiting example of a toe-piece according to the present inventionwill now be described in detail with reference to FIGS. 1 to 9.

As indicated in the Background Information section related to the stateof the art, a binding usually comprises two retaining devices, includinga toe-piece and a heel-piece, for retaining a boot on a gliding board.In the non-limiting example, which will be described below, theretaining device considered is a toe-piece. Alternatively, or incombination, the invention can also be applied to a heel-piece.

The toe-piece 1 comprises a chassis 11, a body 12, and a sole-clamp 13.These elements will be described in detail below.

Chassis 11

The chassis 11 has a lower surface 111 intended to be positionedopposite an upper surface 31 of a gliding board 3. The gliding boardalso has a lower surface 32 intended to be in contact with a substratesuch as snow. The lower surface 111 of the chassis 11 can be fixed tothe upper surface 31 of the gliding board 3 by being either directly incontact with the latter, or by being fixed to the gliding hoard 3 bymeans of another element.

This fixing can eliminate any degree of freedom between the chassis 11and the gliding board 3. To this end, and as is visible in FIGS. 1, 3,and 4, the chassis 11 comprises fixing devices, typically screws 113,that engage with a thread formed in the gliding board 3.

According to an alternative example, this fixing of the chassis 11 tothe gliding board 3 can be provided to allow at least one degree offreedom, for example in translation of the chassis 11 in relation to thegliding board 3. According to this alternative example, the chassis 11can then be provided to be mounted on a rack sliding along alongitudinal axis of the gliding board 3. This allows adjustment of itslongitudinal position. Once the toe-piece is positioned longitudinally,the chassis is blocked from further displacement in all directions. Thechassis is then affixed to the gliding board according to all thedegrees of freedom in this configuration of use.

The chassis 11 also carries a support plate 112, an upper surface ofwhich is intended to come into contact with a portion of a boot 2. Inthe example illustrated, the support plate 112 is configured to receivea front portion 21 of a boot 2. More precisely, the lower surface 213 ofa sole 22 of the boot 2 takes support on the upper surface of thissupport plate 112.

In this example, the chassis 11 is defined by a median longitudinal axisX115 extending along a direction parallel to the X axis. Thelongitudinal axis X115 of the chassis corresponds to the longitudinalaxis of the toe-piece. The longitudinal axis X115 of the chassis, thelongitudinal axis of the gliding board 3 and the X axis aresubstantially parallel.

Body 12

The body 12 of the toe-piece 1 is movably mounted on the chassis 11 andcarries the sole-clamp 13. In the example illustrated, this movabilityis a rotational movability. Alternatively, a translational movability ora movability combining rotational and translational movements can beprovided.

In the example illustrated, the body 12 is rotationally mounted about anaxis of rotation Y122 transverse to the longitudinal axis X115 of thechassis 11. These axes X115, X122 are referenced in particular in FIG.6. They are parallel to the X axis and to the Y axis, respectively, ofthe orthogonal reference point XYZ illustrated in FIGS. 5 and 6. Thus,the body 12 can tilt in relation to the chassis 11 and, consequently, inrelation to the gliding board 3, along an angle α that can be measuredbetween the longitudinal axis X115 of the chassis 11 and a medianlongitudinal axis X121 of the body 12. The median axis X121 of the body12 is contained in a plane parallel or identical to the plane ZX, andthe angle α is measured in this same plane passing through the medianaxis X121 of the body 12. The inclination of the body in relation to thechassis is therefore measured in a vertical plane passing through thelongitudinal axis of the chassis. According to a non-limiting example,the longitudinal axis X115 of the chassis 11 and the median axis X121 ofthe body 12 are included in the same plane, preferably the same verticalplane, preferably the plane ZX.

In FIG. 7, the longitudinal axis X115 of the chassis 11 is parallel to,or even merged with, the median axis X121 of the body 12. The angle α isthen zero. In FIGS. 7 and 8, the median axis X121 of the body isinclined by an angle α (referenced as aa in FIG. 7 and ab in FIG. 8) inrelation to the longitudinal axis X115 of the chassis 11. This angle αincreases when the body 12, in the area of the sole-clamp 13, moves awayfrom the board 3.

The chassis comprises a yoke having two flanges 114 carrying a shaft1221 materializing the axis of rotation Y122. The shaft 1221 can befixed in relation to the yoke of the chassis 11, the body 12 thenrotating about this shaft 1221. Alternatively, the shaft 1221 can beprovided to be fixed in relation to the body 12 and rotationally mountedin the yoke.

In this example, as seen in FIGS. 6 to 8, the axis of rotation Y122 ofthe body 12 is positioned in the area of the upper portion of the body.The yoke thus enables such positioning of the axis of rotation, at acertain height of the upper surface 31 of the gliding board 3. The body12 can thus pivot mainly below this axis of rotation Y122.

Sole Clamp 13

The toe-piece 1 comprises a sole-clamp 13. As indicated above in theBackground Information section related to the state of the art, thesole-clamp 13 has for a function to maintain a portion of the boot 2affixed to the gliding board 3, at least along the vertical andtransverse directions. To this end, the sole-clamp exerts a pressingforce Fp on the portion of the boot 2 in order to maintain it in contactwith the support plate 112. This pressing force Fp is vertical or has avertical component.

In this example, the sole-clamp 13 has a lower support surface 131 androllers 135 configured to come into contact with the boot 2. When theretaining 1 is a toe-piece, the boot portion 2 on which the sole-clamp13 exerts a pressing force is a front portion. Preferably, thesole-clamp 13 is configured so that the lower support surface 131 comesinto contact with an upper surface 211 of the front portion 21 of theboot 2. Preferably, the sole-clamp is also configured so that eachroller 135, and more precisely a portion of the outer cylindricalsurface of a roller 135, comes into contact with a lateral surface 212of this front portion 21 of the boot 2. In the example illustrated inFIG. 2, for example, the front portion 21 of the boot 2 is an integralpart of, or at least partially formed by, a sole 22 of the boot 2.Alternatively, the front portion of the boot can be a portion of aseparate insert attached to the boot.

According to another variant, the sole-clamp acts on a portion of theboot 2 which is distinct from the sole 22 of the boot 2. The termsole-clamp 13 therefore does not necessarily imply a contact of thesole-clamp 13 in the area of a sole of the boot 2. Indeed, the portionof the boot 2 on which the sole-clamp 13 can exert the pressing force Fpmay be a portion of the boot located above the sole 22.

In the example shown, the sole-clamp 13 of the toe-piece comprises twowings 132 arranged on both sides of the median axis X121 of the body 12.As shown in FIG. 5, each wing 132 carries a roller 135 intended to comeinto contact with a lateral surface 212 of the front portion of theboot. Each wing 132 is rotationally mounted on the body 12 about an axisof rotation Z133. This axis of rotation Z133 is substantially vertical,in particular when the median axis X121 of the body 12 is aligned withthe longitudinal axis X115 of the chassis 11. Naturally, this axis ofrotation Z133 tilts with respect to the chassis 11 and therefore withrespect to the vertical when the body 12 pivots about the axis Y122.

In an engagement configuration of the boot 2, each wing 132 of thesole-clamp 13 exerts a pressing force Fp on the boot 2, via the lowersupport surface 131. This pressing force Fp tends to constrain the boot2 between the wing 132 and the support plate 112.

In a variant, the sole-clamp 13 is a unitary part having two arms, eacharm being intended to cover an upper surface and a lateral surface of anedge of the front portion of the boot. The sole-clamp is alsorotationally mounted on the body 12 about an axis of rotation Z,substantially perpendicular to the median axis X121 of the body 12.

Lateral Release Mechanism

The body 12 also comprises a lateral release mechanism configured to:

-   -   retain or return each wing 132 into an engagement configuration        with the boot 2,    -   allow the rotation of each wing 132 about its axis of rotation        Z133 in order to switch to the release configuration when the        force Fd exerted by the boot 2 on the binding is sufficient.        This force, referred to as the release force, is referenced as        Fd in FIG. 5.

More specifically, the release force Fd exerted by the boot 2 on thesole-clamp 13 has at least one component perpendicular to the axis ofrotation Z133 of the wing 132. When this component is sufficient, atleast one of the wings 132 rotates about its axis of rotation Z133. Thisenables a displacement of the front portion of the boot 2 in relation tothe chassis 11 along a substantially lateral direction, that is to sayalong a direction having a horizontal component (Y axis) perpendicularto the longitudinal axis X115 of the chassis 11. In the releaseconfiguration, the wing 132 is no longer in engagement with the frontportion of the boot 2. The boot 2 can then be released from thetoe-piece 1 and from the binding. Typically, it is during a user fallphase that this force Fd enable a switch to the release configuration.The boot can then be separated from the gliding board.

The lateral release mechanism appears in particular in FIGS. 5 and 6.This mechanism comprises a tie rod 146 having a drive surface 147 whichcooperates with a shaft 134 carried by a wing 132 of the sole-clamp 13.On the example shown, the tie rod 146 has two drive surfaces 147 whicheach cooperate with a shaft 134 carried by one of the two wings 132. Thedisplacement of the tie rod 146, along its main direction of extension,causes the displacement of the shaft 134, thereby causing the wing 132to rotate about its axis of rotation Z133. Preferably, the maindirection of extension of the tie rod 146 is coaxial with the medianaxis X121 of the body 12.

The release mechanism also comprises at least one first elasticmechanism 141 configured to return the tie rod 146 to a position wherebythe tie rod 146 brings the wing 132 into the engagement configuration.In the example shown, the first elastic mechanism 141 tends to pull thetie rod 146 towards the front of the body 12, which tends to cause theshaft 134 to rotate about the axis of rotation Z133 so that the roller135 of the wing 132 moves closer, in a horizontal plane, to thelongitudinal axis X115 of the chassis 11. The roller 135 is thenmaintained in or returned to the engagement configuration. When the bootis engaged with the binding, the roller of the left wing presses againstthe left lateral surface of the front portion of the boot, and theroller of the right wing presses against the right lateral surface ofthe front portion of the boot.

For transmission of the force between the first elastic mechanism 141and the tie rod 146, the body 12 can be provided to have a housing 123for receiving at least a portion of the first elastic mechanism 141. Thefirst elastic mechanism 141 has:

-   -   a first end 1411 in support on the body 12, by direct contact or        via an additional part such as a rocker 161, for example. In the        example illustrated, the first end 1411 is in support on a wall        124 of the bottom of the housing 123 via a rocker 161 that will        be described in detail later.    -   a second end 1412 in support on the tie rod 146 or on a part        affixed to the tie rod 146.

Preferably, the first elastic mechanism 141 is a spring working incompression, which may be a coil spring. The first elastic mechanism 141compresses as the wings open or, in other words, as the rollers 135 ofthe wing 132 move away from the median axis X121 of the body 12 along adirection transverse to this axis median X121. This compression occursalong a working axis X142. This working axis X142 is preferably parallelto or merged with the median axis X121 of the body 12.

In the example illustrated, the tie rod 146 is affixed to a Sleeve 148within which the first elastic mechanism 141 is housed at leastpartially. The sleeve 148 has a bottom wall 1481 on which the second end1412 of the first elastic mechanism 141 takes support. Advantageously,an adjustment member 149 is provided to make it possible to vary thedistance between the shafts 134 and the second end 1412 of the firstelastic mechanism 141. This adjustment member 149 makes it possible toadjust the compression ratio of the first elastic mechanism 141 when thewings 132 are in the engagement configuration. Therefore, it makes itpossible to adjust the force that the user must exert to space the wingsapart and switch to the release configuration. Typically, the adjustmentmember 149 makes it possible to adjust the “DIN value” as has beendefined above. The adjustment member 149 can be manipulated by the userby means of a tool. In the example shown, the adjustment member 149 hasa recess for cooperation with a tool and can form a screw head.

In this example, as seen in FIGS. 6 to 8, the axis of rotation Y122 ofthe body 12 is positioned in the area of the upper portion of the body,above the first elastic mechanism 141 of the lateral release mechanism14.

Vertical Retention Mechanism

As indicated above, to affix the boot 2 vertically to the gliding board,the boot is clamped between the support surface 131 of the sole-clamp13, that is to say, the combination of the support surfaces of thewings, and the support plate 112 of the chassis 11. Thus, the sole-clamp13 exerts a pressing force Fp on the boot 2 via the sole-clamp. Thefollowing paragraphs provide a detailed description of the kinematicsthat makes it possible to control this pressing force Fp, irrespectiveof the angle α that the body 12 forms in relation to the chassis 11.Subsequently, the position of the sole-clamp 13 in relation to the platesupport 112 corresponds to the vertical position (along a Z axis) of thesupport surfaces 131 of the wings 132 of the sole-clamp 13 in relationto the horizontal surface tangent to the upper surface of the supportplate 112. This position is directly related to the inclination α of thebody 12 carrying the sole-clamp. The distancing of the sole-clamp 13from the support plate 112 therefore corresponds to an increase in thevertical distance H, projection on a Z axis, between the supportsurfaces 131 and the support plate.

To this end, the toe-piece 1 comprises a vertical retention mechanism.This mechanism comprises at least one second elastic mechanism 151configured to exert a return force Fr1 on the body 12. This return forceFr1 tends to return the support surfaces 131 of the wings 132 of thesole-clamp 13 towards the gliding board 3, more precisely towards thesupport plate 112 resting on the gliding board 3. In more detail, thereturn force Fr1 is exerted along a substantially vertical directionthat makes it possible to generate a torque M on the body 12 about itsaxis of rotation Y122. This torque generates the pressing force Fp onthe shoe 2 in the area of the support surface 131 of the sole-clamp 13.

The second elastic mechanism 151 can be carried either by the body 12,as is the case in the embodiment of FIGS. 1 to 9, or by the chassis 11,as is the case in the embodiment illustrated in FIG. 10. In these twoembodiments, the second elastic mechanism 151 is configured so that thechassis 11 generates a return force Fr1 on the body 12.

In the example illustrated in FIG. 7, the median axis X121 of the body12 is inclined by an angle αa in relation to the longitudinal axis X115of the chassis 11 and the return force is referenced as Fr1 a. Theproduct of the intensity of the force Fr1 a multiplied by the distanceD1 a between the direction of the force Fr1 a and the axis of rotationY122 is equal to the value of the torque Ma generated by the force Fr1 aon the body 12. Thus, Ma=Fr1 a×D1 a. In the absence of compensationmeans, described below, the intensity of the pressing force Fpa exertedby the sole-clamp 13 on the boot 2 is equal to this torque Ma divided bythe distance Dp between the direction of the pressing force Fpa and theaxis of rotation Y122. Thus, Fpa=Ma/Dp=Fr1 a/(D1 a×Dp).

FIG. 7 illustrates the references Fr1 a, D1 a, Ma, Fpa, Dp.

The second elastic mechanism 151 is configured so that the intensity ofthe return force Fr1 resulting from the action of the second elasticmechanism increases when the sole-clamp 13 moves away from the supportplate 112. Preferably, the second elastic mechanism 151 is a springworking in compression, which may be a coil spring. It compresses as thesole-clamp 13 moves away from the support plate 112. This compressionoccurs along a working axis X152. According to one example, this workingaxis X152 is parallel to the median axis X121 of the body 12.Preferably, this working axis X152 is parallel but not coaxial with theworking axis X142 of the first elastic mechanism 141. These two axes areincluded, for example, in the same vertical plane ZX.

In the non-limiting example illustrated in FIGS. 1 to 9, the body has ahousing 127 shaped to receive a part, acting as a piston 155, capable oftranslating in the housing 127. This piston has a head 158 and a body156. The body forms a sleeve 156, open at one of its ends and having aninner support wall 157 at the other one of its ends. The second elasticmechanism 151 is partially housed within the sleeve 156. A first end1511 of the second elastic mechanism 151 is in support on a wall 128 ofa housing 127 carried by the body 12. A second end 1512 of the secondelastic mechanism 151 is in support on the support wall 157 of thepiston 155. The force exerted by the compression of the second elasticmechanism 151 therefore tends to move the head 158 of the piston 155away from the wall 128 of the body 12. The head 158 of the piston 155has an outer surface intended to come into contact with an extension 116of the chassis 11 or a part carried by the chassis.

The return force Fr1 resulting from the action of the second elasticmechanism 151, between the chassis 11 and the body 12, is applied in thearea of the contact between the head 158 of the piston 155 and theextension 116.

Furthermore, the extension 116 and the head 158 of the piston 155 areconfigured such that, when the body 12 pivots about the axis of rotationY122, the piston 155 is displaced in the housing 127 thus causing avariation in the compression of the second elastic mechanism 151.Consequently, the intensity of the return force Fr1 varies, as afunction of the inclination of the body 12 in relation to the chassis11. More precisely, in this case, when the body 12 pivots so as toincrease the angle α, the extension 116 compresses the second elasticmechanism 151, thereby increasing the intensity of the return force Fr1exerted by the chassis 11 on the body 12 via the piston 155.

Attenuation Device

According to a particular advantage, the toe-piece 1 comprises anattenuation device configured so as to reduce the increase in theintensity of the pressing force Fp1 caused by the sole-clamp 13 beingmoved away from the support plate 112.

Typically, the attenuation device makes it possible to limit thevariation in the intensity of the pressing force Fp1 to a maximum of20%, preferably to a maximum of 10%, and preferably to a maximum of 5%over the entire travel of the body 12 in relation to the chassis 11.

According to one embodiment, the variation in the intensity of thepressing force Fp1 varies in an interval between −20% and +10%,preferably in an interval between −15% and +5%.

According to an example of embodiment, the intensity of the pressingforce Fp1 remains constant irrespective of the position of the body 12in relation to the chassis 11, in this example irrespective of the valueof the angle α formed between the median axis X121 of the body 12 andthe longitudinal axis X115 of the chassis 11. For this example ofembodiment, as the distance Dp between the point of application of thepressing force Fp of the sole-clamp 13 on the boot 2 and the axis ofrotation Y122 of the body 12 is substantially constant, the intensity ofthe torque Ma, Mb is substantially constant irrespective of the positionof the body 12 with respect to the chassis 11.

The angle α is dictated by the distance H, in projection along thevertical direction Z and in the engagement configuration, between theupper surface of the support plate 112 and the point of application ofthe pressing force Fp of the sole-clamp 13 on the boot 2. This distanceis referenced as:

-   -   H0 in FIG. 6 and corresponds to the configuration of the        toe-piece in the absence of a boot;    -   Ha in FIG. 7 and corresponds to the distance imposed by a boot        of a first type, for example an alpine ski boot; and    -   Hb in FIG. 8 and corresponds to the distance imposed by a boot        of a second type, for example a ski touring boot.

In this example, the toe-piece is configured so that:

-   -   When no boot is engaged with the toe-piece, the angle α is equal        to 0°, and the clamping height corresponds to the reference        height H0.    -   When a boot of a first type, for example an alpine ski boot, is        engaged with the toe-piece, the angle α is equal to 1.5°, and        the clamping height Ha corresponds to the reference height        H0+1.3 mm.    -   When a boot of a second type, for example a ski touring boot, is        engaged with the toe-piece, the angle α is equal to 5.5°, and        the clamping height Hb corresponds to the reference height        H0+5.7 mm.

Furthermore, the toe-piece comprises a stop device which makes itpossible to limit the inclination of the body 12. Thus, in this example,the angle α is equal to a maximum of 8°, and the clamping height Hmcorresponds to the reference height H0+8.2 mm.

The toe-piece is therefore designed such that the body 12 can tilt by amaximum angle α of 15°, preferably a maximum angle of 10°. In otherwords, the toe-piece is designed such that the body 12 can tilt so thatthe maximum clamping height Hm corresponds to the reference height H0+15mm, preferably a maximum height corresponding to the reference heightH0+10 mm.

Thus, irrespective of the dimensions of the boot portion 2, intended tobe inserted into the toe-piece 1, the torque M as well as the pressingforce Fp exerted by the sole-clamp 13 on this boot portion 2 remainconstant or within a small interval. Thus, during a lateral release, thevariation in the friction exerted by the sole-clamp 13 on the boot 2also remains constant or within a small interval. The threshold value ofthe release force Fd necessary for switching to the releaseconfiguration therefore also remains constant or within a small intervalregardless of these boot dimensions. User safety is therefore preservedregardless of the boots used with the same toe-piece 1.

To be able to reduce the increase in the intensity of the pressing forceFp1 caused by the sole-clamp 13 moving away from the support plate 112,the attenuation device is configured to modify the distance D1 betweenthe direction of application of the return force Fr1 and the axis ofrotation Y122 of the body 12. In this example, the distance D1 decreasesat the same time as the return force Fr1 increases and the sole-clamp 13moves away from the support plate 112.

To this end, the attenuation device comprises a cam, also referred to asa cam device, arranged on one of the parts enabling the transfer of thereturn force Fr1 from the chassis 11 to the body 12. This cam is shapedto vary the distance D1.

In the example illustrated in FIGS. 1 to 9, this cam is kinematicallyarranged between the second elastic mechanism 151 and the chassis 11.The cam can be arranged in other locations. For example, in anembodiment that will be described in detail with reference to FIG. 10,the cam can be arranged between the second elastic mechanism 151 and thebody 12.

In the example illustrated in FIGS. 1 to 9, the cam device is formed bythe cooperation of the extension 116 affixed to the chassis 11 and theouter surface of the piston 155. These parts 116, 155 are shaped suchthat the distance D1, as defined above, is reduced as the angle α formedby the inclination of the body 12 in relation to the chassis 11increases. In this example, the outer surface of the head 158 of thepiston 155 forms a first cam profile 153. Furthermore, the extension 116forms a second cam profile 154 intended to cooperate with the first camprofile 153. Variants can naturally be envisioned. For example, one ofthe extension 116 and outer surface of the piston 155 could be providedto have a continuous surface and only the other one of the extension 116and outer surface of the piston 155 to have a cam profile.

According to this embodiment, the cam therefore has a first cam profile153 affixed to the body 12 in rotation about the axis of rotation Y122,and a second cam profile 154 affixed to the chassis 11.

The cam profiles 153, 154 are shaped such that the direction of thereturn force Fr1 approaches the axis of rotation Y122 as the distance Himposed by the boot 2 on the toe-piece 1 increases.

FIGS. 7 and 8 particularly clearly illustrate the operation of thisattenuation device.

In FIG. 7, the boot 2 used imposes a distance Ha between the supportplate 112 of the chassis 11 and the support surface 131 of thesole-clamp 13. As a result, the body 12 has an inclination aa inrelation to the chassis 11. The chassis 11 exerts a return force Fr1 aon the body 12, via the extension 116, due to the second elasticmechanism 151. The relative position of the first and second camprofiles 153, 154 of the cam device dictate the direction along whichthis return force Fr1 a is exerted. This cam device therefore dictatesthe distance D1 a between the direction of this return force Fr1 a andthe center of rotation Y122 of the body 12. Consequently, this camdevice has an impact on the intensity of the pressing force Fpa exertedby the sole-clamp 13 on boot 21, because Fpa=Ma/Dp=Fr1 a/(D1 a×Dp), asindicated above.

In FIG. 8, the boot 2 used imposes a distance Hb, with Hb>Ha, betweenthe support plate 112 of the chassis 11 and the support surface 131 ofthe sole-clamp 13. As a result, the body 12 has an inclination αb, withαb>αa, in relation to the chassis 11. The chassis 11 exerts a returnforce Fr1 b on the body 12 by means of the extension 116, due to thesecond elastic mechanism 151. The relative position of the first andsecond cam profiles 153, 154 of the cam device dictates the directionalong which this return force Fr1 b is exerted. This cam devicetherefore dictates the distance D1 b between the direction of thisreturn force Fr1 b and the center of rotation 122 of the body 12. Asclearly appears in FIGS. 7 and 8, D1 b<D1 a. The intensity of the returnforce Fpb exerted by the sole-clamp 13 on the boot 2 is such thatFpb=Mb/Dp=Fr1 b/(D1 b×Dp).

The second elastic mechanism 151 and the cam device are configured suchthat the difference between D1 b and D1 a, on the one hand, and thedifference between Fr1 b and Fr1 a, on the other hand, are such that theintensities of the return forces Fpb and Fpa are identical atapproximately 20%, preferably at approximately 10%, preferably atapproximately 5%. According to one embodiment, the intensities of thereturn forces Fpb and Fpa vary in an interval between −20% and +10%,preferably in an interval between −15% and +5%.

Compensation Mechanism

According to an optional but particularly advantageous exemplaryembodiment, the toe-piece 1 comprises a compensation mechanism. Thiscompensation mechanism is configured to adapt the pressing force Fp as afunction of the adjustment made on the lateral release mechanism 14.More precisely, this compensation mechanism makes it possible toautomatically increase the value of the pressing force Fp when the useradjusts the lateral release mechanism 14 to increase the lateral releasethreshold value.

Thus, according to one embodiment:

-   -   due to the attenuation device described above, for the same        adjustment value of the lateral release threshold, typically the        same DIN value, the pressing force Fp remains constant        irrespective of the angle α, therefore irrespective of the        dimension H of the boot 2. This scenario is illustrated in FIG.        9A: at constant DIN, Fp remains constant irrespective of the        inclination of the body 12, irrespective of the value of the        angle α;    -   due to the compensation mechanism, for two adjustment values of        the lateral release threshold, typically for two DIN values, the        pressing force Fp varies, for the same inclination of the body        12, i.e., for the same value of the angle α. This scenario is        also shown in FIG. 9A: if the DIN value increases, then Fp        increases. Indeed, when the user increases the DIN value, he may        wish to have a firmer hold of his boot in the binding and seek        to obtain more substantial threshold value of the release force        Fd and pressing force Fp. In the absence of the compensation        mechanism, an increase in the threshold value of the release        force Fd, an increase desired by the user, is not accompanied by        an increase in the pressing force Fp. The compensation mechanism        makes it possible to overcome this drawback.

At the same time, as illustrated in FIG. 9B, the lateral releasethreshold value Fd increases slightly the more the body is inclined,that is to say, when the angle α increases, but the value of the DINadjustment remains constant. Furthermore, the lateral release thresholdvalue Fd increases significantly when the user increases the value ofthe DIN adjustment, in this example by going from a DIN 11 adjustment toa DIN 16 adjustment.

As illustrated in FIG. 8, the compensation mechanism exerts anadditional return force Fr2 b on the body 12, which generates a torqueM2 b on the body 12, about its axis of rotation Y122. The distancebetween the direction of this additional return force Fr2 b and the axisof rotation Y122 is referenced as D2 b. Thus, the torque M2 b is equalto: M2 b=Fr2 b×D2 b. Moreover, as seen above, the second elasticmechanism 151 also exerts a return force Fr1 b on the body 12, whichtranslates into a torque M1 b equal to M1 b=Fr1 b×D1 b. Thus, the torqueexerted on the body is the sum of the two previous torques and is equalto: Mb=M1 b+M2 b. The pressing force Fpb is directly proportional to thetorque Mb and is equal to: Frp=Mb/Dp. The value of the pressing forceFpb exerted by the sole-clamp 13 on the boot 2 is then deducedtherefrom, which is equal to: Fpb=Fr1 b/(D1 b×Dp)+Fr2 b/(D2 b×Dp).

The compensation mechanism comprises a rocker 161 shown in perspectivein FIGS. 3 and 4. This rocker 161 is configured to be partially housedin the housing 123 of the body 12 receiving the first elastic mechanism141, The rocker 161 is configured to rotate within the body 12, about adirection substantially perpendicular to the working axis X142 of thefirst elastic mechanism 141. Typically, the rocker 161 is configured torotate, over a small angular sector, about a direction transverse to themedian axis X121 of the body 12. To this end, the rocker preferablycomprises a pivot portion 1611 configured to be housed in a seat 125formed in the wall 124 of the housing 123.

In this construction, as mentioned above, the rocker is inserted betweenthe first end 1411 of the first elastic mechanism 141 and the body 12.The first elastic mechanism therefore takes support on the rocker. Thus,when the rocker is pivoted, the first elastic mechanism is acted upon,by compressing it, for example, when the rocker pivots in one direction.

The rocker 161 also comprises a support portion 1612 interposed betweenthe second end 1412 of the first elastic mechanism 141 and the wall 124of the bottom of the housing 123 of the body 12. Thus, the first elasticmechanism 141 takes support in particular on this support portion 1612.

Preferably, the pivot portion 1611 and the support portion 1612 arelocated on both sides of the working axis X142. To this end, the rocker161 comprises an opening 1615 shaped to be crossed through by the tierod 144.

The rocker 161 also comprises an extension 1616 extending beyond thebody 12 to come into contact with a portion 117 of the chassis 11 or apart carried by the chassis.

At least either the rocker 161 or the portion 117 of the chassis has acam profile. In the example shown, the extension 1616 carries a camprofile 1613 that cooperates with a profile 1614 having the generalshape of a slope and carried by the portion 117 of the chassis.

As shown in FIG. 7, that is to say with a boot 2 that causes the body 12to tilt in relation to the chassis 11 by a low angle αa (“low” boot 2),the cooperation between the cam surface 1613 and the profile 114 enablesthe support portion 1612 to be maintained in its seat 126, that is tosay, in a position in which this support portion 1612 does not, or onlyslightly does, constrain the first elastic mechanism 141. In thisexample, with the angle αa, the cam profile 1613 maintains the supportportion 1612 pressed in a seat 126 formed in the wall 124 of the body12. The rocker 161 does not compress the first elastic mechanism 141.

Conversely, as illustrated in FIG. 8, that is to say with a shoe 2 whichcauses the body 12 to tilt in relation to the chassis 11 by a high angleαb (“high” boot 2), the cooperation between the cam surface 1613 and ofthe profile 114 causes the support portion 1612 to move away from itsseat 126. This translates into in the compression of the first elasticmechanism 141. This results in a return force Fr2 b which, with thereturn force Fr1 b, contributes to generating a torque Mb on the body12, about its axis of rotation Y122. This torque Mb exerts the pressingforce Fpb of the sole-clamp 13 on the boot 2. Moreover, as the firstelastic mechanism 141 is more strongly compressed, the threshold valueof the release force Fd increases, as illustrated in FIG. 9B.

Thus, FIGS. 7 and 8 illustrate the contribution of the return force Fr2exerted by the compensation mechanism on the pressing force Fp. Thesefigures also clearly illustrate the compression imposed by thiscompensation mechanism on the first elastic mechanism 141, and thereforeon the threshold value of the release force Fd (typically the DINvalue).

As indicated above, this compensation mechanism is optional, and thetoe-piece is fully operational without such a mechanism.

Alternative Embodiment

An alternative embodiment will now be described with reference to FIGS.10 and 11. With the exception of the details are be provided below, allthe characteristics, advantages and technical effects mentioned abovewith respect to the embodiment of FIGS. 1 to 9 are fully transposable toand combinable with the embodiment described with reference to FIGS. 10and 11.

The hatching used for FIGS. 10 and 11 may vary without implyingstructural differences. Furthermore, in FIG. 10, a thread 1461 is shownon a portion of the tie rod 146, this thread 1461 cooperating with theadjustment member 149 described with reference to the embodimentillustrated in FIGS. 1 to 9.

In this embodiment, the second elastic mechanism 151 is carried by thechassis 11, unlike the first embodiment in which the second elasticmechanism 151 is carried by the body 12. More precisely, this firstelastic mechanism has one end in support on a support wall 119 affixedto the chassis 11, and another end in support on a support wall 157carried by a piston 155 slidably translationally mounted on the chassis11. This translation occurs along an axis parallel to the longitudinalaxis X115 of the chassis 11. Thus, the body 12 is in rotation inrelation to the second elastic mechanism 151.

The piston 155 has a surface 154 sliding in relation to the chassis 11and in relation to the axis of rotation Y122 of the body 12. The body 12has a surface 153 shaped to remain in contact with the surface 154. Thereturn force Fr1 a exerted by the second elastic mechanism 151 isapplied to the body 12 in the area of the contact between the surfaces153 and 154. Thus, these surfaces 153, 154 are kinematically insertedbetween the second elastic mechanism 151 and the body 12.

FIG. 10 illustrates the toe-piece in the lower position, that is to sayin a position in which it is biased by a first boot category. The medianaxis X121 of the body is therefore inclined in relation to thelongitudinal axis X115 of the chassis 11 by a non-zero inclination angleαa.

FIG. 11 illustrates the toe-piece in the upper position, that is to sayin a position in which it is biased by a second boot category. Themedian axis X121 of the body is therefore inclined in relation to thelongitudinal axis X115 of the chassis 11 by a non-zero inclination angleαb.

According to this alternative embodiment, the cam has a first camprofile 153 affixed to the body 12, and a second cam profile 154 carriedby the chassis 11 and preferably being slidably mounted on the chassis11.

These surfaces 153 and 154 are configured to form the cam device of theattenuation device described above. At least one of these surfaces 153,154 has a cam profile such that an increase in the inclination of thebody 12 in relation to the chassis 11 (so as to move the sole-clamp 13away from the support plate 112), causes:

-   -   a greater compression of the second elastic mechanism 151, and    -   a variation in the direction of application of the return force        Fr1 a, Fr1 b exerted on the body 12, due to the second elastic        mechanism 151, by means of the cooperation between the surfaces        153 and 154, this variation in direction tending to reduce the        distance D1 (D1 b<D1 a) between this direction and the axis of        rotation Y122 of the body 12.

Thus, for this embodiment, as for that described with reference to FIGS.1 to 9, the attenuation device makes it possible to limit, or evencancel the variation in the intensity of the pressing force Fp when thebody 12 tilts in relation to the chassis 11. Without an attenuationdevice according to the invention, the intensity of the pressing forceFp tends to vary proportionally as a function of the inclination of thebody in relation to the chassis. Consequently, the attenuation devicemakes it possible to control the pressing force Fp according to theinclination of the body and, in particular, to avoid having asubstantial pressing force Fp at the end of the body travel.

With the configurations of the non-limiting examples described above, itis noted that the second elastic mechanism 151 is arranged so as to acton the body 12, that is to say to exert a return force Fr1 thereon,irrespective of the position of the sole-clamp 13 in relation to thebody 12. Furthermore, it is noted that the second elastic mechanism 151acts on the body 12 independently of the action exerted by thesole-clamp 13 on the first elastic mechanism. Thus, the first elasticmechanism and the second elastic mechanism act completely independently.

Examples of Possible Variants

The invention is not limited to the embodiments described above butextends to all of the embodiments covered by the claims.

The invention also applies to constructions combining some or all of thefeatures characterizing the embodiments described above.

According to a variant, the first elastic mechanism extendstransversely, along a direction Y.

For example, although, in the detailed description and the drawingfigures, the retaining device incorporating the cam is a bindingtoe-piece, the invention also extends to a heel-piece, also referred toas the binding heel-piece.

Furthermore, although, in the detailed description, the movability ofthe body 12 in relation to the chassis 11 is a rotational movabilityabout the axis of rotation 122, the invention also extends to aconfiguration in which the body 12 is movable translationally inrelation to the chassis 11 or is movable according to a combination ofrotational and translational movement in relation to the chassis 11.

In the above description, the non-limiting examples may relate to agliding board forming a ski and a ski boot. The invention extends togliding boards other than skis, for example snowboards and footwearsuitable for snowboards.

Furthermore, in the preceding example, the retaining device, alsoreferred to as the sole-clamp 13, comprises two wings 132 pivotallymounted on the body, each pivoting about a respective axis of rotation.Nevertheless, the two wings can be provided to be affixed rotationally.For example, they can form a generally U-shaped or V-shaped unitaryelement mounted rotationally about a single axis on the body 12.

Moreover, in the above example, the vertical retention mechanismcomprises a single second elastic mechanism. Nevertheless, this verticalretention mechanism can be provided to comprise two or more secondelastic mechanism. For example, two springs arranged on both sides ofthe median axis X121 of the body 12, and each cooperating with a camprofile, can be provided.

Further, at least because the various embodiments of the invention aredisclosed herein in a manner that enables one to make and use them asdescribed and shown, such as for simplicity or efficiency, for example,the invention can be practiced in the absence of any additional elementor additional structure that is not specifically disclosed herein.

The invention claimed is:
 1. Toe-piece for binding a boot on a glidingboard comprising: a chassis having a lower surface configured to beaffixed to the gliding board; a body movably mounted on the chassis; asole-clamp movably mounted on the body and capable of coming intocontact with an upper surface and at least one lateral portion of afront or rear portion of the boot, when the boot is engaged with thetoe-piece; a lateral release mechanism comprising at least one firstelastic mechanism acting on the sole-clamp to return the sole-clamp to aconfiguration of engagement with the boot; a vertical retentionmechanism comprising a second elastic mechanism, distinct from the firstelastic mechanism, arranged so as to always exert a return force on thebody in order to bring the sole-clamp back toward the lower surface ofthe chassis, the return force producing a force pressing the sole-clampon the boot when the boot is engaged with the binding; at least one camkinematically inserted between the second elastic mechanism and eitherthe chassis or the body; the cam having a shape configured to modify,depending on a position of the body in relation to the chassis, adirection of the return force exerted by the second elastic mechanism onthe body so as to attenuate a variation in the pressing force when thesole-clamp is moved away from the lower surface of the chassis. 2.Toe-piece according to claim 1, wherein: the body is pivotally mountedon the chassis about an axis of rotation crosswise to a longitudinalaxis of the chassis; the cam has a shape configured to modify thedirection of the return force exerted by the second elastic mechanism onthe body so that a distance between the direction of the return forceand the axis of rotation of the body differs as a function of the angleof inclination of the body in relation to the chassis.
 3. Toe-pieceaccording to claim 2, wherein: the axis of rotation of the body ispositioned in an area of the upper portion of the body, above the firstelastic mechanism of the lateral release mechanism.
 4. Toe-pieceaccording to claim 1, wherein: the second elastic mechanism is carriedby the body.
 5. Toe-piece according to claim 1, wherein: the cam and thevertical retention mechanism have shapes configured so that the pressingforce does not vary by more than 20%, regardless of the position of thesole-clamp in relation to the body.
 6. Toe-piece according to claim 1,wherein: the cam and the vertical retention mechanism have shapesconfigured so that the pressing force does not vary by more than 10%,regardless of the position of the sole-clamp in relation to the body. 7.Toe-piece according to claim 1, wherein: the second elastic mechanism isarranged so as to act always on the body, regardless of the position ofthe sole-clamp in relation to the body.
 8. Toe-piece according to claim1, wherein: the second elastic mechanism is arranged so as to act on thebody independently of the action of the sole-clamp on the first elasticmechanism of the lateral release mechanism.
 9. Toe-piece according toclaim 1, wherein: the first elastic mechanism is configured to bealternately compressed and relaxed along a first working axis; thesecond elastic mechanism is configured to be alternately compressed andrelaxed along a second working axis, said second working axis beingmisaligned with respect to said first working axis.
 10. Toe-pieceaccording to claim 1, wherein: a first profile of the cam istranslationally mounted on the body.
 11. Toe-piece according to claim10, wherein: the second elastic mechanism acts directly on a pistoncapable of translating in a housing of the body, a portion of the pistonforming a first profile of the cam.
 12. Toe-piece according to claim 1,wherein: the sole-clamp comprises two wings, each wing being pivotallymounted on the body.
 13. Toe-piece according to claim 1, wherein: thecam is dimensioned such that the return torque exerted on the body, andwherein by the product of the intensity of the return force multipliedby the distance between the direction of the return force and the axisof rotation of the body, is, when the at least one sole-clamp is awayfrom the gliding board, identical, at approximately 20% to this returntorque when the sole-clamp is close to the lower surface of the chassis.14. Toe-piece according to claim 1, wherein: the cam is dimensioned suchthat the return torque exerted on the body, and wherein by the productof the intensity of the return force multiplied by the distance betweenthe direction of the return force and the axis of rotation of the body,is, when the at least one sole-clamp is away from the gliding board,identical, at approximately 10% to this return torque when thesole-clamp is close to the lower surface of the chassis.
 15. Toe-pieceaccording to claim 1, wherein: the lateral release mechanism comprisesan adjustment device configured to enable adjustment of a thresholdvalue of a release force to be applied to the lateral release mechanismto cause the sole-clamp to switch to a lateral release configuration,the toe-piece also comprising a compensation mechanism configured toexert an additional return force on the body, the intensity of theadditional return force being a function of said adjustment, thepressing force being a function of the return force exerted by thesecond elastic mechanism and of the additional return force exerted bythe compensation, mechanism.
 16. Gliding hoard in combination with atleast one toe-piece according to claim
 1. 17. Toe piece for binding aboot on a gliding hoard comprising: a chassis having a lower surfaceconfigured to be affixed to the gliding board; a body movably mounted onthe chassis; a sole-clamp movably mounted on the body and capable ofcoming into contact with art upper surface and at least one lateralportion of a front or rear portion of the boot, when the boot is engagedwith the toe-piece; a lateral release mechanism comprising at least onefirst elastic mechanism acting on the sole-clamp to return thesole-clamp to a configuration of engagement with the boot; a verticalretention mechanism comprising a second elastic mechanism, distinct fromthe first elastic mechanism, arranged so as to continuously exert areturn force on the body in order to bring the sole-clamp back towardthe lower surface of the chassis, the return force producing a forcepressing the sole-clamp on the hoot when the boot is engaged with thebinding; at least one cam kinematically inserted between the secondelastic mechanism and either the chassis or the body; the cam having ashape configured to modify, depending on a position of the body inrelation to the chassis, a direction of the return force exerted by thesecond elastic mechanism on the body so as to attenuate a variation inthe pressing force when the sole-clamp is moved away from the lowersurface of the chassis wherein: the body is pivotally mounted on thechassis about an axis of rotation crosswise to a longitudinal axis ofthe chassis; the cam has a shape configured to modify the direction ofthe return force exerted by the second elastic mechanism on the body sothat a distance between the direction of the return force and the axisof rotation of the body differs as a function of the angle ofinclination of the body in relation to the chassis; and wherein: theaxis of rotation of the body is positioned in an area of the upperportion of the body, above the first elastic mechanism of the lateralrelease mechanism.